EP1925838A1 - Manschette für homokinetische kupplung - Google Patents

Manschette für homokinetische kupplung Download PDF

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Publication number
EP1925838A1
EP1925838A1 EP06797789A EP06797789A EP1925838A1 EP 1925838 A1 EP1925838 A1 EP 1925838A1 EP 06797789 A EP06797789 A EP 06797789A EP 06797789 A EP06797789 A EP 06797789A EP 1925838 A1 EP1925838 A1 EP 1925838A1
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EP
European Patent Office
Prior art keywords
peak
valley
section
boot
diameter section
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06797789A
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English (en)
French (fr)
Other versions
EP1925838A4 (de
EP1925838B1 (de
Inventor
Tsuyoshi Ueno
Mikio Tomiyama
Shintaro Harada
Tomonari Oosumi
Atsuto Takemura
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NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of EP1925838A1 publication Critical patent/EP1925838A1/de
Publication of EP1925838A4 publication Critical patent/EP1925838A4/de
Application granted granted Critical
Publication of EP1925838B1 publication Critical patent/EP1925838B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/84—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor
    • F16D3/843—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor enclosed covers
    • F16D3/845—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor enclosed covers allowing relative movement of joint parts due to the flexing of the cover
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/2237—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts where the grooves are composed of radii and adjoining straight lines, i.e. undercut free [UF] type joints
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J3/00—Diaphragms; Bellows; Bellows pistons
    • F16J3/04—Bellows
    • F16J3/041—Non-metallic bellows
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22316—Means for fastening or attaching the bellows or gaiters

Definitions

  • the present invention relates to a boot for a constant velocity universal joint.
  • the present invention relates to a boot for a constant velocity universal joint used for power transmission in automobiles and various industrial machineries.
  • a bellows-like boot is attached to a constant velocity universal joint used for power transmission in automobiles and various industrial machineries.
  • the bellows-like boot aims to prevent ingress of foreign objects, such as dust, into an interior of the joint and leakage of grease enclosed in the interior of the joint.
  • a resin boot made from a thermoplastic elastomer is recently being used.
  • this type of boot includes a large diameter section 102, a small diameter section 105, and a bellows section 108.
  • the large diameter section 102 is fixed onto an outer ring 101 of a constant velocity universal joint 100.
  • the small diameter section 105 is fixed onto a shaft 104 that extends from an inner ring 103.
  • the bellows section 108 is provided between the large diameter section 102 and the small diameter section 105. Alternating valleys 106 and peaks 107 are formed in the bellows section 108.
  • the large diameter section 102 and the small diameter section 105 are respectively fixed by a boot band 109 being fitted onto the large diameter section 102 and the small diameter section 105.
  • a valley 106 closest to the large diameter section 102 is not in contact with the outer ring 101.
  • the valley 106 closest to the large diameter section 102 may become caught between an opening end section and the shaft 104 at an opening section 101a of the outer ring 101 and become damaged.
  • the boot cannot function as a boot, thereby requiring replacement or the like. Therefore, in a conventional boot such as that shown in Fig. 3 , a diameter of the valley 106 is required to be large to prevent the valley 106 from becoming caught between the opening end section and the shaft 104.
  • a cylindrical section is provided between the large diameter section and the bellows section (Patent Document 1).
  • a cylindrical section 111 having a larger inner diameter dimension than an outer diameter dimension of the outer ring 101 is provided between the large diameter section 102 and the bellows section 108.
  • a thickness of the cylindrical section 111 is thicker than a thickness of the bellows section 108.
  • a boot in which the diameter of the cylindrical section 111 is successively widened from the large diameter section 102 side towards the small diameter section 105 side.
  • the boot flexes in an outer radial direction, as indicated by a phantom line, thereby preventing the valley 106 from becoming caught.
  • Patent Document 2 and Patent Document 3 There is also a boot in which various boot thicknesses are set to prevent friction caused by rubbing within the bellows section in the bent joint state, thereby achieving enhancement in abrasion resistance.
  • Patent Document 4 There is also a boot that bends in adherence to the bending of the joint, thereby preventing damage and achieving an enhancement in fatigability from flexing.
  • Patent Document 1 Japanese Utility Model Application Publication No. 2525619
  • Patent Document 2 Japanese Utility Model Laid-Open Publication No. Heisei 7-10561
  • Patent Document 3 Japanese Utility Model Laid-Open Publication No. Heisei 6-82463
  • Patent Document 4 Japanese Patent Laid-open Publication No.
  • Patent Document 5 Japanese Patent Laid-open Publication No. Heisei 6-129536
  • Patent Document 6 Japanese Patent Laid-open Publication No. Heisei 8-135675
  • Patent Document 7 Japanese Utility Model Laid-Open Publication No. Heisei 7-38758
  • the peak 107 is required to be designed to be higher to ensure bellows length (bellows film length). Therefore, a maximum outer diameter of the bellows section increases, thereby causing a spatial disadvantage.
  • an axial direction length of the cylindrical section 111 is required to be relatively long. Therefore, an axial direction length of the entire boot increases. As a result, the numbers and disposal pitches of valleys 106 and peaks 107 in the bellows section 108 may be restricted, and flexibility and stretchability may deteriorate.
  • Patent Document 2 In the boots described in Patent Document 2, Patent Document 3 and the like, abrasion resistance is enhanced. In Patent Document 4 to Patent Document 7 and the like, fatigability from flexing is enhanced, thereby extending life of the boot. Therefore, a boot such as those described in these Patent Documents and the like cannot prevent the bellows section from becoming caught in the outer ring opening section.
  • the present invention provides a boot for a constant velocity universal joint that is compact in shape and can prevent a bellows section from becoming caught in an outer ring opening section.
  • a boot for a constant velocity universal joint of the present invention includes a large diameter section that is attached to an opening end section of an outer joint component of a constant velocity universal joint, a small diameter section that is attached to a shaft connected to an inner joint component of the constant velocity universal joint, and a bellows section that is provided between the large diameter section and the small diameter section and has peaks and valleys alternately disposed in an axial direction.
  • a peak is provided adjacent to the large diameter section and to the small diameter section.
  • a peak and valley of an axial direction center section as reference, thicknesses of peaks and valleys to the small diameter section side of the reference peak and valley are thinner than reference thickness of the reference peak and valley and thicknesses of peaks and valleys to the large diameter section side of the reference peak and valley are thicker than the reference thickness of the reference peak and valley.
  • the thickness of the peak adjacent to the large diameter section is the reference thickness.
  • the peak is provided adjacent to the large diameter section and to the small diameter section.
  • the thicknesses of the peaks and valleys to the small diameter section side of the reference peak and valley are thinner than the reference thickness of the reference peak and valley, and the thicknesses of peaks and valleys to the large diameter section side of the reference peak and valley are thicker than the reference thickness of the reference peak and valley.
  • the thickness of the peak adjacent to the large diameter section is the reference thickness.
  • a valley closest to the large diameter section can be displaced such as to prevent becoming caught between an opening end section of the outer ring and the shaft.
  • the thicknesses of the peaks thicker than the reference thickness are preferably thicker than the thicknesses of the valleys thicker than the reference thickness.
  • the bellows section has seven peaks and six valleys, and third peak and valley from the small diameter section are the reference.
  • the thicknesses of the peaks and valleys can be increased or decreased within a range of 85% to 115%.
  • a difference between the thicknesses m and r of two arbitrarily selected peaks 16 and valleys 17 is preferably kept constant.
  • thermoplastic elastomer of an ester series, olefin series, urethane series, amide series, styrene series, and the like can be used as a boot material.
  • the present invention can prevent the valley of the bellows section from becoming caught between the opening end section of the opening section of the outer ring and the shaft. As a result, damage to the bellows section caused by jamming on the joint side can be prevented.
  • the boot can function as a boot for a long period of time. Because jamming is prevented, the outer diameter dimension is not required to be large. An interference range with peripheral devices can be reduced. Freedom in boot design increases. A design can be made in which the diameter of the valley closest to the large diameter section (position closest to the large diameter section) is made smaller than (lowered from) a track section diameter of the outer ring and a bellows length (bellows film length) is secured. A design having overall compactness in the radial direction and the axial direction can be made.
  • the thicknesses of the peaks and valleys can be increased or decreased within the range of 85% to 115%. Therefore, high dimensional accuracy is not really required, and simplification of manufacturing can be achieved.
  • the constant velocity universal joint boot 1 has superior strength and is advantageous in terms of abrasion resistance.
  • a constant velocity universal joint boot 1 is attached to a constant velocity universal joint 2, as shown in Fig. 1 .
  • the constant velocity universal joint 2 includes an outer joint member (outer ring) 4, an inner joint member (inner ring) 6, a plurality of balls 7, a holder 8, and the like.
  • a plurality of guiding grooves (track grooves) 3 are formed on an inner circumferential surface of the outer ring 4 in an axial direction.
  • a plurality of guiding grooves (track grooves) 5 are formed on an outer circumferential surface of the inner ring 6.
  • the balls 7 are placed on ball tracks formed through coordination between the guiding grooves 3 of the outer ring 4 and the guiding grooves 5 of the inner ring 6.
  • the holder 8 has pockets 8a for storing the balls 7.
  • a shaft 10 is connected to an inner circumference of the inner ring 6, via a torque transmitting means, such as serration or a spline.
  • a spline forming section 25 on which a spline 24 is formed is provided on an end section of the shaft 10.
  • the spline forming section 25 being inserted into a center hole of the inner ring 6, the spline 24 of the shaft 10 and a spline 26 formed on an inner circumferential surface of the inner ring 6 are engaged.
  • a stopper ring groove 27 is formed on the spline forming section 25 within an axial direction range of the spline 24.
  • a stopper ring 28 is engaged with the stopper ring groove 27, forming a dislocation stopping mechanism.
  • the constant velocity universal joint 2 is merely required to be that to which the constant velocity universal joint boot 1 can be attached. Therefore, various kinds of constant velocity universal joints can be used, for example, fixed constant velocity universal joints such as a Rzeppa-type or a Birfield-type, or slide-type constant velocity universal joints such as a double-offset-type, a tri-port-type, or a cross-groove-type.
  • fixed constant velocity universal joints such as a Rzeppa-type or a Birfield-type
  • slide-type constant velocity universal joints such as a double-offset-type, a tri-port-type, or a cross-groove-type.
  • the constant velocity universal joint boot 1 (sometimes referred to, hereinafter, as simply boot 1) is formed by, for example, a thermoplastic elastomer of an ester series, olefin series, urethane series, amide series, styrene series, and the like.
  • the thermoplastic elastomer has characteristics that are between plastic and rubber. While the thermoplastic elastomer is a rubber elastic body, the thermoplastic elastomer can be processed by an ordinary thermoplastic resin molding machine.
  • the thermoplastic elastomer has advantages such as having self-reinforcement properties, having sufficient strength without use of reinforcing materials, not requiring a vulcanizing procedure during ordinary rubber molding, and furthermore, achieving simplified composition.
  • the constant velocity universal joint boot 1 is formed from a cylindrical body and includes a large diameter section 11, a small diameter section 12, and a bellows section 13.
  • the large diameter section 11 is fixed onto the outer ring 4.
  • the small diameter section 12 is fixed onto the shaft 10 extending from the inner ring 6.
  • the bellows section 13 is provided between the large diameter section 11 and the small diameter section 12.
  • a plurality of valleys 15 and peaks 16 are alternately disposed in the bellows section 13 along an axial direction. Therefore, the boot 1 is provided with flexibility and stretchability in the axial direction.
  • a valley 15 and a peak 16 are connected by a sloping section 17.
  • a ring-shaped engaging groove 20 is formed in a circumferential direction on an outer circumferential surface on an opening side of the outer ring 4.
  • the large diameter section 11 of the boot 1 is fitted outside of the opening side of the outer ring 4 such as to cover the engaging groove 20.
  • a boot band 21 is fitted and attached to a fitting groove 18 formed on an outer circumferential surface of the large diameter section 11, thereby fixing the large diameter section 11 onto the outer ring 4.
  • a boot attaching section 22 is provided in a position on the shaft 10 that projects from the outer ring 4 by a predetermined amount.
  • the boot attaching section 22 has a ring-shaped engaging groove 23 along the circumferential direction.
  • the small diameter section 12 of the boot 1 is fitted outside of the boot attaching section 22 such as to cover the engaging groove 23.
  • the boot band 21 is fitted and attached to a fitting groove 19 formed on an outer circumferential surface of the small diameter section 12, thereby fixing the small diameter section 12 onto the shaft 10.
  • the bellows section 13 of the boot 1 has seven peaks 16 and six valleys 15. Therefore, the peak 16 is provided adjacent to the large diameter section 11 and to the small diameter section 12.
  • the peaks 16 from the small diameter section 12 towards the large diameter section 11 are sequentially referred to as a first peak 16a, a second peak 16b, a third peak 16c, a fourth peak 16d, a fifth peak 16e, a sixth peak 16f, and a seventh peak 16g.
  • the valleys 15 are sequentially referred to as a first valley 15a, a second valley 15b, a third valley 15c, a fourth valley 15d, a fifth valley 15e, and a sixth valley 15f.
  • thicknesses m and r (see Fig. 2 ) of the peaks and valleys 16 and 15 to the small diameter section 12 side of the reference peak and valley 16 and 15 are thinner than a reference thickness of the reference peak and valley 16 and 15. Thicknesses of the peaks and valleys 16 and 15 to the large diameter section 11 side of the reference peak and valley 16 and 15 are thicker than the reference thickness. Furthermore, a thickness m of the peak 16 (seventh peak 16g) adjacent to the large diameter section 11 is the reference thickness.
  • each peak 16 and the thickness r of each valley 15 are set as shown in a following Table 1.
  • A indicates the reference thickness.
  • A can be arbitrarily set depending on a boot material being used and the like.
  • a thickness m3 of the third peak 16c and a thickness r3 of the third valley 15c are the reference thickness.
  • Thickness r1 of the first valley 15a and thickness r2 of the second valley 15b are each about 0.15 millimeters thinner than the reference thickness A.
  • Thickness r4 of the fourth valley 15d, thickness r5 of the fifth valley 15e, and thickness r6 of the sixth valley 15f are each about 0.1 millimeters larger than the reference thickness A.
  • the peak 16 is provided adjacent to the large diameter section 11 and to the small diameter section 12.
  • the thicknesses of the peaks and valleys 16 and 15 to the small diameter section 12 side of the reference peak and valley 16 and 15 are thinner than the reference thickness of the reference peak and valley 16 and 15.
  • the thicknesses of the peaks and valleys 16 and 15 to the large diameter section 11 side of the reference peak and valley 16 and 15 are thicker than the reference thickness.
  • the thickness of the peak adjacent to the large diameter section is the reference thickness.
  • the valley 15 closest to the large diameter section 11 can be displaced such as to prevent becoming caught between an opening end section 4a of the outer ring 4 and the shaft 10.
  • the valley 15 of the bellows section 13 can be prevented from becoming caught between the opening end section 4a of the outer ring 4 and the shaft 10 in the bent joint state. Therefore, damage to the bellows section 13 caused by jamming on the joint side can be prevented.
  • the boot can function as a boot for a long period of time. Because jamming is prevented, the outer diameter dimension is not required to be large. An interference range with peripheral devices can be reduced. Freedom in boot design increases.
  • a design can be made in which the diameter of the valley 15 closest to the large diameter section (position closest to the large diameter section) is made smaller than (lowered from) a track section diameter of the outer ring 4 and a bellows length (bellows film length) is secured.
  • a design having overall compactness in the radial direction and the axial direction can be made.
  • the constant velocity universal joint boot 1 has superior strength and is advantageous in terms of abrasion resistance.
  • the thickness m and r of the peaks and valleys 16 and 15 can be increased or decreased within a range of 85% to 115%. In this case, a difference between the thicknesses m and r of two arbitrarily selected peaks 16 and valleys 17 is preferably kept constant.
  • the thicknesses m and r are increased or decreased and the thicknesses m and r set as shown in Table 1 are used as reference, when, for example, the thicknesses m and r reduced to 85%, the reference thicknesses m and r, and the thicknesses m and r increased to 115% are compared, a difference in the thicknesses of two arbitrary peaks 16 and valleys 15 regarding the thicknesses m and r that are reduced to 85%, a difference in the thicknesses of two arbitrary peaks 16 and valleys 15 regarding the reference thicknesses m and r, and a difference in the thicknesses of two arbitrary peaks 16 and valleys 15 regarding the thicknesses m and r that are increased to 115% are each set to be the same.
  • the thickness of the first peak 16a is m11
  • the thickness of the second peak 16b is m12
  • a thickness of an n-th peak 16n is m1n regarding the reference thicknesses m and r
  • the thickness of the first peak 16a is m21
  • the thickness of the second peak 16b is m22
  • a thickness of an n-th peak 16n is m2n regarding the thicknesses m and r that are reduced to 85%
  • the thickness of the first peak 16a is m31
  • the thickness of the second peak 16b is m32
  • a thickness of an n-th peak 16n is m3n regarding the thicknesses m and r that are increased to 115%
  • the thickness of the first valley 15a is r11, the thickness of the second valley 15b is r12, and so on such that a thickness of an n-th valley 15n is r1n regarding the reference thicknesses m and r
  • the thickness of the first valley 15a is r21, the thickness of the second valley 15b is r22, and so on such that a thickness of an n-th valley 15n is r2n regarding the thicknesses m and r that are reduced to 85%
  • the thickness of the first valley 15a is r31, the thickness of the second valley 15b is r32, and so on such that a thickness of an n-th valley 15n is r3n regarding the thicknesses m and r that are increased to 115%
  • a relationship in a following Equation 2 is realized.
  • the thicknesses of the peaks and valleys can be increased or decreased within the range of 85% to 115%. Even when the thicknesses are increased or decreased, the valley 15 of the bellows section 13 can be prevented from becoming caught between the opening end section 4a of the outer ring 4 and the shaft 10 in the bent joint state. Therefore, in the boot 1, high dimensional accuracy is not really required, and simplification of manufacturing can be achieved. To prevent the boot 1 from getting caught (jammed), the difference between the thicknesses m and r of two arbitrarily selected peaks 16 and valleys 15 is preferably kept constant.
  • the third peak 16c, the fourth peak 16d, the seventh peak 16g, and the third valley 15c are set to be the reference thickness A.
  • the first peak 16a, the second peak 16b, the first valley 15a, and the second valley 15b are set to be about 0.1 millimeters thinner than the reference thickness A.
  • the fifth peak 16e and the sixth peak 16f are set to be about 0.05 millimeters thicker than the reference thickness A.
  • the fourth valley 15d, the fifth valley 15e, and the sixth valley 16f are set to be about 0.1 millimeters thicker than the reference thickness A.
  • the boot material is preferably a thermoplastic elastomer.
  • the boot material can be other kinds of resin or rubber.
  • a material having moderate flexibility, strength, sealing properties, and durability is preferably selected.
  • the increase and decrease of the number of peaks and valleys 16 and 15 are arbitrary.
  • the peak and valley 16 and 15 to be the reference is not limited to the third peak and valley 16 and 15.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Diaphragms And Bellows (AREA)
  • Sealing Devices (AREA)
EP06797789.2A 2005-09-16 2006-09-11 Manschette für homokinetische kupplung Not-in-force EP1925838B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005270358A JP4832837B2 (ja) 2005-09-16 2005-09-16 等速自在継手用ブーツ
PCT/JP2006/317963 WO2007032301A1 (ja) 2005-09-16 2006-09-11 等速自在継手用ブーツ

Publications (3)

Publication Number Publication Date
EP1925838A1 true EP1925838A1 (de) 2008-05-28
EP1925838A4 EP1925838A4 (de) 2009-09-23
EP1925838B1 EP1925838B1 (de) 2017-05-31

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EP06797789.2A Not-in-force EP1925838B1 (de) 2005-09-16 2006-09-11 Manschette für homokinetische kupplung

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US (1) US20090214286A1 (de)
EP (1) EP1925838B1 (de)
JP (1) JP4832837B2 (de)
CN (1) CN101292092B (de)
WO (1) WO2007032301A1 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101696622A (zh) * 2009-10-23 2010-04-21 上海佳友市政建筑有限公司 可变角传动的单动接头
CN105387092A (zh) * 2015-12-15 2016-03-09 天津市环宇橡塑股份有限公司 一种带有5波峰和5波谷结构的驱动轴固定端cvj防尘罩
CN105351381A (zh) * 2015-12-15 2016-02-24 天津市环宇橡塑股份有限公司 一种带有8波峰结构的驱动轴伸缩端cvj防尘罩

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Also Published As

Publication number Publication date
EP1925838A4 (de) 2009-09-23
CN101292092A (zh) 2008-10-22
CN101292092B (zh) 2010-08-11
US20090214286A1 (en) 2009-08-27
JP2007078148A (ja) 2007-03-29
WO2007032301A1 (ja) 2007-03-22
JP4832837B2 (ja) 2011-12-07
EP1925838B1 (de) 2017-05-31

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